WO2024262005A1 - Heat exchange device - Google Patents

Abstract

A heat exchange device (100) comprises a heat exchanger (HE) and a centrifugal blower (CB). The centrifugal blower (CB) has a first blowing unit (B1), a second blowing unit (B2), and a rotating shaft (S). The first blowing unit (B1) has a first impeller (I1). The second blowing unit (B2) has a second impeller (I2). The rotating shaft (S) extends in a first direction (D1) in which the first impeller (I1) and the second impeller (I2) face each other, and is connected to the first impeller (I1) and the second impeller (I2). A first heat exchange unit (H1) surrounds the first blowing unit (B1) in a second direction (D2) and is disposed on the side that is opposite the second blowing unit (B2) with respect to the first blowing unit (B1), in the first direction (D1). A second heat exchange unit (H2) surrounds the second blowing unit (B2) in the second direction (D2) and is disposed on the side that is opposite the first blowing unit (B1) with respect to the second blowing unit (B2), in the first direction (D1).

Description

Heat Exchange Equipment

This disclosure relates to heat exchange equipment.

In the past, indoor units equipped with multiple centrifugal fans have been proposed to increase the amount of heat exchanged. For example, JP 2000-46360 A (Patent Document 1) describes a ceiling-embedded indoor unit equipped with two centrifugal fans. The two centrifugal fans are lined up in the radial direction of the centrifugal fans. A U-shaped heat exchanger is arranged around the two centrifugal fans. The U-shaped side of the heat exchanger extends along the direction in which the two centrifugal fans are lined up.

JP 2000-46360 A

In the indoor unit described in the above publication, the U-shaped side of the heat exchanger extends along the direction in which the two centrifugal fans are lined up, but there is room for improvement in the heat transfer area of the heat exchanger.

This disclosure has been made in consideration of the above problems, and its purpose is to provide a heat exchange device that can improve the heat transfer area of a heat exchanger.

The heat exchange device of the present disclosure includes a heat exchanger and a centrifugal blower configured to blow air to the heat exchanger. The centrifugal blower has a first blowing section, a second blowing section, and a rotating shaft. The first blowing section has a first impeller. The second blowing section has a second impeller. The second impeller faces the first impeller. The rotating shaft extends in a first direction in which the first impeller and the second impeller face each other and is connected to the first impeller and the second impeller. The heat exchanger has a first heat exchange section and a second heat exchange section. The first heat exchange section sandwiches the first blowing section in a second direction perpendicular to the first direction and is positioned on the opposite side of the second blowing section to the first blowing section in the first direction. The second heat exchange section is disposed between the second blower section in the second direction and on the opposite side of the second blower section from the first blower section in the first direction.

The heat exchange device disclosed herein can improve the heat transfer area of the heat exchanger.

1 is a refrigerant circuit diagram of a refrigeration cycle device according to a first embodiment. FIG. 1 is a perspective view showing a schematic configuration of a heat exchanger according to a first embodiment; 1 is a top view illustrating a schematic configuration of a heat exchanger according to a first embodiment. FIG. 1 is a perspective view showing a schematic configuration of a centrifugal blower of a heat exchanger according to a first embodiment of the present invention; 5 is a cross-sectional view taken along line VV in FIG. 4. FIG. 13 is a top view illustrating a schematic configuration of a modified example of the heat exchanger according to the first embodiment. FIG. 11 is a top view illustrating a schematic configuration of a heat exchanger according to a second embodiment. FIG. 11 is a top view illustrating a schematic configuration of a heat exchanger according to a first modified example of the second embodiment. FIG. 11 is a top view illustrating a schematic configuration of a second modified example of a heat exchanger according to the second embodiment. FIG. 11 is a top view illustrating a schematic configuration of a third modified example of a heat exchanger according to the second embodiment. FIG. 11 is a top view illustrating a schematic configuration of a heat exchanger according to a third embodiment. FIG. 13 is a top view illustrating a schematic configuration of a heat exchanger according to a first modified example of the third embodiment. FIG. 13 is a top view illustrating a schematic configuration of a heat exchanger according to a second modified example of the third embodiment. FIG. 13 is a top view illustrating a schematic configuration of a heat exchanger according to a fourth embodiment. FIG. 13 is a top view illustrating a schematic configuration of a heat exchanger according to a fifth embodiment.

Below, an embodiment will be described with reference to the drawings. Note that in the drawings, the same or corresponding parts are given the same reference numerals and their description will not be repeated.

Embodiment 1.
The configuration of a refrigeration cycle apparatus according to a first embodiment will be described with reference to Fig. 1. In this embodiment, an air conditioner 1000 will be described as an example of a refrigeration cycle apparatus. The solid arrows in Fig. 1 indicate the flow of refrigerant during cooling operation. The dashed arrows in Fig. 1 indicate the flow of refrigerant during heating operation.

As shown in FIG. 1, the air conditioner 1000 includes an outdoor unit 101 and an indoor unit 102. The heat exchanger 100 according to embodiment 1 is applied to the outdoor unit 101. The heat exchanger 100 according to embodiment 1 may also be applied to the indoor unit 102. The air conditioner 1000 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 4, an indoor heat exchanger 5, an outdoor blower 6, an indoor blower 7, and a control device 8. The heat exchanger HE according to embodiment 1 is applied to the outdoor heat exchanger 3. The heat exchanger HE according to embodiment 1 may also be applied to the indoor heat exchanger 5. The centrifugal blower CB according to embodiment 1 is applied to the outdoor blower 6. The centrifugal blower CB according to embodiment 1 may also be applied to the indoor blower 7. The compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, outdoor blower 6, and control device 8 are housed in the outdoor unit 101. The indoor heat exchanger 5 and indoor blower 7 are housed in the indoor unit 102.

The refrigerant circuit 10 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion valve 4, and an indoor heat exchanger 5. The refrigerant circuit 10 is configured so that during cooling operation, the refrigerant circulates in the order of the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, the indoor heat exchanger 5, and the four-way valve 2. During heating operation, the refrigerant circuit 10 is configured so that the refrigerant circulates in the order of the compressor 1, the four-way valve 2, the indoor heat exchanger 5, the expansion valve 4, the outdoor heat exchanger 3, and the four-way valve 2. The compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion valve 4, and the indoor heat exchanger 5 are connected by piping 20. Part of the piping 20 constitutes the gas pipe 21 and the liquid pipe 22. The outdoor unit 101 and the indoor unit 102 are connected by the gas pipe 21 and the liquid pipe 22.

The compressor 1 is configured to compress the refrigerant. The compressor 1 is for compressing the refrigerant flowing into the outdoor heat exchanger 3 or the indoor heat exchanger 5. The compressor 1 is configured to compress the refrigerant that is sucked in and discharge it. The compressor 1 may be configured to have a variable capacity. The compressor 1 may be configured so that the capacity can be changed by adjusting the rotation speed of the compressor 1 based on instructions from the control device 8.

The four-way valve 2 is configured to switch the flow of the refrigerant compressed by the compressor 1 to the outdoor heat exchanger 3 or the indoor heat exchanger 5. The four-way valve 2 is configured to be switchable so that the refrigerant discharged from the compressor 1 flows to the outdoor heat exchanger 3 during cooling operation, and the refrigerant discharged from the compressor 1 flows to the indoor heat exchanger 5 during heating operation.

The outdoor heat exchanger 3 is configured to exchange heat between the refrigerant flowing inside the outdoor heat exchanger 3 and the air flowing outside the outdoor heat exchanger 3. The outdoor heat exchanger 3 is configured to function as a condenser that condenses the refrigerant during cooling operation, and as an evaporator that evaporates the refrigerant during heating operation.

The expansion valve 4 is configured to reduce the pressure of the refrigerant condensed in the condenser by expanding it. The expansion valve 4 is configured to reduce the pressure of the refrigerant condensed by the outdoor heat exchanger 3 during cooling operation, and to reduce the pressure of the refrigerant condensed by the indoor heat exchanger 5 during heating operation. The expansion valve 4 is, for example, an electromagnetic expansion valve.

The indoor heat exchanger 5 is configured to exchange heat between the refrigerant flowing inside the indoor heat exchanger 5 and the air flowing outside the indoor heat exchanger 5. The indoor heat exchanger 5 is configured to function as an evaporator that evaporates the refrigerant during cooling operation, and as a condenser that condenses the refrigerant during heating operation.

The outdoor blower 6 is configured to blow outdoor air to the outdoor heat exchanger 3. In other words, the outdoor blower 6 is configured to supply outdoor air to the outdoor heat exchanger 3. The indoor blower 7 is configured to blow indoor air to the indoor heat exchanger 5. In other words, the indoor blower 7 is configured to supply indoor air to the indoor heat exchanger 5.

The control device 8 is configured to perform calculations, instructions, etc. to control each device of the air conditioner 1000. The control device 8 is electrically connected to the compressor 1, four-way valve 2, expansion valve 4, outdoor blower 6, indoor blower 7, etc., and is configured to control the operation of these devices.

Next, the operation of the air conditioner 1000 according to the first embodiment will be described with reference to FIG.

The air conditioner 1000 can selectively perform cooling operation and heating operation. During cooling operation, the refrigerant circulates through the refrigerant circuit 10 in the order of compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valve 4, indoor heat exchanger 5, and four-way valve 2. During cooling operation, the outdoor heat exchanger 3 functions as a condenser. During cooling operation, the indoor heat exchanger 5 functions as an evaporator. During heating operation, the refrigerant circulates through the refrigerant circuit 10 in the order of compressor 1, four-way valve 2, indoor heat exchanger 5, expansion valve 4, outdoor heat exchanger 3, and four-way valve 2. During heating operation, the indoor heat exchanger 5 functions as a condenser. During heating operation, the outdoor heat exchanger 3 functions as an evaporator. Heat exchange occurs between the refrigerant flowing through the outdoor heat exchanger 3 and the air blown by the outdoor blower 6. Heat exchange occurs between the refrigerant flowing through the indoor heat exchanger 5 and the air blown by the indoor blower 7.

The configuration of the heat exchange device 100 will be described in detail with reference to Figures 2 and 3. In Figure 2, for ease of viewing, the housing of the heat exchange device 100 is shown with dashed lines. In Figure 3, for ease of viewing, the housing of the heat exchange device 100 is not shown. The heat exchange device 100 includes a heat exchanger HE and a centrifugal blower CB. The centrifugal blower CB is configured to blow air to the heat exchanger HE.

The centrifugal blower CB has a first blowing section B1, a second blowing section B2, and a rotating shaft S. The first blowing section B1 has a first impeller I1. The second blowing section B2 has a second impeller I2. The second impeller I2 faces the first impeller I1. The rotating shaft S extends in a first direction D1 in which the first impeller I1 and the second impeller I2 face each other. The first direction D1 is the direction in which the first impeller I1 and the second impeller I2 face each other. The first direction D1 is also the direction in which the rotating shaft S extends. The rotating shaft S is connected to the first impeller I1 and the second impeller I2. The rotating shaft S is connected to the rotation centers of the first impeller I1 and the second impeller I2. The rotation axis S extends in a direction perpendicular to the radial direction of the first impeller I1 and the second impeller I2. An air outlet is provided on the upper surface of each of the first blower section B1 and the second blower section B2.

The heat exchanger HE has a first heat exchange section H1 and a second heat exchange section H2. In this embodiment, the first heat exchange section H1 and the second heat exchange section H2 are arranged separately. The first heat exchange section H1 sandwiches the first air blowing section B1 in a second direction D2 perpendicular to the first direction D1, and is arranged on the opposite side of the second air blowing section B2 with respect to the first air blowing section B1 in the first direction D1. The second direction D2 is a direction perpendicular to the first direction D1. The first heat exchange section H1 sandwiches the first air blowing section B1 in the second direction D2, and has a side portion extending in the first direction D1. The first heat exchange section H1 is arranged on the opposite side of the second air blowing section B2 with respect to the first air blowing section B1 in the first direction D1, and has a bottom portion extending in the second direction D2. A portion of the first heat exchange section H1 is positioned so as to intersect with an extension of the rotation axis S in the direction in which the rotation axis S extends.

The second heat exchange section H2 sandwiches the second air blowing section B2 in the second direction D2 and is arranged on the opposite side of the first air blowing section B1 with respect to the second air blowing section B2 in the first direction D1. The second heat exchange section H2 sandwiches the second air blowing section B2 in the second direction D2 and has a side extending in the first direction D1. The second heat exchange section H2 is arranged on the opposite side of the first air blowing section B1 with respect to the second air blowing section B2 in the first direction D1 and has a bottom extending in the second direction D2. A part of the second heat exchange section H2 is arranged so as to intersect with an extension of the rotation axis S in the direction in which the rotation axis S extends.

The first impeller I1 and the second impeller I2 are configured to be rotatable by the rotation of the rotating shaft S. The first impeller I1 and the second impeller I2 are configured to be rotatable about a common rotating shaft S. The first blowing section B1 and the second blowing section B2 are configured to be able to blow air by the rotation of the common rotating shaft S. The rotating shaft S is configured to be rotated by, for example, a motor.

At least one of the first heat exchange section H1 and the second heat exchange section H2 is configured to protrude toward the rotation axis S between the first air blowing section B1 and the second air blowing section B2. At least one of the first heat exchange section H1 and the second heat exchange section H2 has a protruding section that protrudes obliquely toward the rotation axis S between the first air blowing section B1 and the second air blowing section B2. At least one of the first heat exchange section H1 and the second heat exchange section H2 is inclined between the first air blowing section B1 and the second air blowing section B2 so as to approach the rotation axis S as it approaches the tip. In this embodiment, both the first heat exchange section H1 and the second heat exchange section H2 are configured to protrude toward the rotation axis S between the first air blowing section B1 and the second air blowing section B2. The tip of each of the first heat exchange section H1 and the second heat exchange section H2 may be configured to close the gap with the rotation axis S. Additionally, a member configured to close the gap with the rotating shaft S may be provided at the tip of each of the first heat exchanger H1 and the second heat exchanger H2.

In this embodiment, the first blower B1 has a first housing C1. The second blower B2 has a second housing C2. The first housing C1 houses the first impeller I1. The second housing C2 houses the second impeller I2.

The configuration of the centrifugal blower CB will be described in detail with reference to Figures 4 and 5. In Figure 4, the rotating shaft S is not shown for ease of viewing. Each of the first impeller I1 and the second impeller I2 has a main plate MP and a number of blades BL. The main plate MP is connected to the rotating shaft S. The main plate MP is configured in a circular plate shape. The multiple blades BL are arranged circumferentially around the rotating shaft S on the main plate MP.

The first housing C1 and the second housing C2 each have an intake port AI and an exhaust port AO. The intake port AI is connected to a space SP in which the main plate MP and the multiple blades BL are arranged. The intake port AI is provided in the bell mouth BM of each of the first housing C1 and the second housing C2. The intake port AI is provided on the side of each of the first housing C1 and the second housing C2. The exhaust port AO is connected to the space SP. The centrifugal blower CB is configured such that, as the first impeller I1 and the second impeller I2 rotate, air sucked in from the intake port AI in each of the first housing C1 and the second housing C2 passes through the space SP and is exhausted from the exhaust port AO.

Next, the effects of the heat exchanger 100 according to the first embodiment will be described.
According to the heat exchanger 100 according to the first embodiment, the first heat exchanger H1 sandwiches the first blower B1 in the second direction D2 perpendicular to the first direction D1, and is disposed on the opposite side of the first blower B1 to the second blower B2 in the first direction D1. The second heat exchanger H2 sandwiches the second blower B2 in the second direction D2, and is disposed on the opposite side of the first blower B1 to the second blower B2 in the first direction D1. Therefore, a part of the first heat exchanger H1 and the second heat exchanger H2 is disposed in the first direction D1. Therefore, the heat transfer area of the heat exchanger HE can be enlarged. Therefore, the heat transfer area of the heat exchanger HE can be improved.

According to the heat exchange device 100 of the first embodiment, the first impeller I1 and the second impeller I2 are configured to be rotatable by the rotation of the rotating shaft S. Therefore, the first impeller I1 and the second impeller I2 can be rotated on a common rotating shaft S. Therefore, it is possible to rotate the first impeller I1 and the second impeller I2 by rotating the rotating shaft S with a motor. Therefore, it is possible to increase the air volume by increasing the number of impellers while using only one motor to rotate the rotating shaft S.

According to the heat exchange device 100 of the first embodiment, at least one of the first heat exchange section H1 and the second heat exchange section H2 is configured to protrude toward the rotation axis S between the first blower section B1 and the second blower section B2. Therefore, the heat transfer area of the heat exchanger HE can be increased by the refrigerant exchanging heat with the air in the protruding portion. This makes it possible to improve the heat exchange performance.

According to the heat exchange device 100 of embodiment 1, the centrifugal blower CB is configured such that, as the first impeller I1 and the second impeller I2 rotate, air sucked in from the intake port AI in each of the first housing C1 and the second housing C2 passes through the space SP and is exhausted from the exhaust port AO. By widening the intake area of the intake port AI in the first housing C1 and the second housing C2 of the centrifugal blower CB, it becomes possible to suck in air over a wide intake area. Therefore, the blowing performance can be improved.

Next, a modified example of the heat exchange device 100 according to the first embodiment will be described with reference to FIG. 6.

In a modified example of the heat exchange device 100 according to the first embodiment, the first heat exchange section H1 and the second heat exchange section H2 are integrally configured. One end of each of the first heat exchange section H1 and the second heat exchange section H2 is connected to each other, and the other end of each of the first heat exchange section H1 and the second heat exchange section H2 is disposed apart from each other. In addition, one end of each of the first heat exchange section H1 and the second heat exchange section H2 is not configured to protrude toward the rotation axis S between the first air blowing section B1 and the second air blowing section B2. On the other hand, the other end of each of the first heat exchange section H1 and the second heat exchange section H2 is configured to protrude toward the rotation axis S between the first air blowing section B1 and the second air blowing section B2.

In the modified example of the heat exchange device 100 according to the first embodiment, the first heat exchange section H1 and the second heat exchange section H2 are integrally configured, which makes it easier to manufacture the heat exchanger HE.

According to a modified example of the heat exchange device 100 according to the first embodiment, one end of each of the first heat exchange section H1 and the second heat exchange section H2 is not configured to protrude toward the rotation axis S, and the other end of each of the first heat exchange section H1 and the second heat exchange section H2 is configured to protrude toward the rotation axis S. This reduces the number of steps required to configure the protrusions. This makes it easier to manufacture the heat exchanger HE.

Embodiment 2.
Unless otherwise specified, the heat exchanger 100 according to the second embodiment has the same configuration, operation, and effects as the heat exchanger 100 according to the first embodiment.

Referring to FIG. 7, the heat exchange device 100 according to the second embodiment has a motor M. The motor M is for driving the centrifugal blower CB. The motor M is configured to rotate the rotating shaft S.

At least a part of the motor M is arranged on the opposite side of the second heat exchange section H2 to the first heat exchange section H1 in the first direction D1. At least a part of the motor M is arranged on the opposite side of the second heat exchange section H2 to the first heat exchange section H1 in the direction in which the rotation axis S extends. The motor M is arranged in a hole provided in the second heat exchange section H2.

According to the heat exchange device 100 of the second embodiment, at least a part of the motor M is arranged on the opposite side of the first heat exchange section H1 with respect to the second heat exchange section H2 in the first direction D1. Therefore, since at least a part of the motor M is arranged outside the heat exchanger HE, when the heat exchange device 100 functions as a condenser, it is possible to prevent the hot air that has exchanged heat with the refrigerant in the heat exchange device 100 from being applied to the motor M. This makes it possible to prevent a decrease in efficiency due to a rise in the temperature of the motor M. In addition, the motor M can be cooled by the air that is sucked into the second heat exchange section H2.

Next, with reference to Figures 8 to 10, we will explain variants 1 to 3 of the heat exchanger 100 according to embodiment 2.

Referring to FIG. 8, in the first modification of the heat exchange device 100 according to the second embodiment, the entire motor M is disposed on the opposite side of the second heat exchange section H2 from the first heat exchange section H1 in the first direction D1. The rotating shaft S is connected to the motor M through a hole provided in the second heat exchange section H2. The motor M is disposed outside the heat exchanger HE.

According to the first modification of the heat exchange device 100 of the second embodiment, the entire motor M is disposed on the opposite side of the first heat exchange section H1 with respect to the second heat exchange section H2 in the first direction D1. Therefore, since the motor M is disposed outside the heat exchanger HE, when the heat exchange device 100 functions as a condenser, it is possible to further prevent the hot air that has exchanged heat with the refrigerant in the heat exchange device 100 from being applied to the motor M. This makes it possible to further prevent a decrease in efficiency due to a rise in temperature of the motor M.

Referring to FIG. 9, in variant 2 of the heat exchange device 100 according to embodiment 2, the motor M is disposed between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1, and is disposed with a gap between the first heat exchange section H1 and the second heat exchange section H2. The motor M is disposed approximately in the center between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1. The motor M is disposed near the center between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1. The motor M does not have to be disposed exactly in the center between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1. The distance L1 in the first direction D1 between the motor M and the first heat exchange section H1 may or may not be the same as the distance L2 in the first direction D1 between the motor M and the second heat exchange section H2. The distance L1 in the first direction D1 between the motor M and the first heat exchanger H1 and the distance L2 in the first direction D1 between the motor M and the second heat exchanger H2 are greater than zero.

According to the second modification of the heat exchange device 100 of the second embodiment, the motor M is disposed between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1, and is disposed with a gap between the first heat exchange section H1 and the second heat exchange section H2. Therefore, when the heat exchange device 100 functions as a condenser, it is possible to prevent the motor M from becoming too hot due to the high-temperature air that has exchanged heat with the refrigerant in the first heat exchange section H1 and the second heat exchange section H2 coming into contact with the motor M. This makes it possible to prevent a decrease in efficiency due to a rise in temperature of the motor M.

Referring to FIG. 10, according to the third modification of the heat exchange device 100 of the second embodiment, the motor M is disposed between the first blower B1 and the second blower B2 in the first direction D1, and is disposed so as to overlap at least one of the first heat exchanger H1 and the second heat exchanger H2 in the second direction D2. The motor M is disposed so as to be covered by at least one of the first heat exchanger H1 and the second heat exchanger H2. The tip of the protruding portion of the first heat exchanger H1 is disposed on the side of the motor M farthest from the first heat exchanger H1, rather than the side of the motor M closest to the first heat exchanger H1. In this embodiment, the motor M is disposed so as to be covered by both the first heat exchanger H1 and the second heat exchanger H2. The tip of the protruding portion of the second heat exchanger H2 is disposed on the side of the motor M farthest from the second heat exchanger H2, rather than the side of the motor M closest to the second heat exchanger H2.

According to the third modification of the heat exchange device 100 of the second embodiment, the motor M is disposed between the first blower B1 and the second blower B2 in the first direction D1, and is disposed so as to overlap with at least one of the first heat exchanger H1 and the second heat exchanger H2 in the second direction D2. Therefore, when the heat exchange device 100 functions as an evaporator, the cooled air that has exchanged heat with the refrigerant in at least one of the first heat exchanger H1 and the second heat exchanger H2 comes into contact with the motor M, thereby lowering the temperature of the motor M. This makes it possible to suppress a temperature rise due to heat generation by the motor M. This makes it possible to suppress a decrease in efficiency due to a temperature rise of the motor M.

Embodiment 3.
Unless otherwise specified, the heat exchanger 100 according to the third embodiment has the same configuration, operation, and effects as the heat exchanger 100 according to the second embodiment.

Referring to FIG. 11, in the heat exchange device 100 according to the third embodiment, the motor M is disposed between the first impeller I1 and the second impeller I2 in the first direction D1, and is disposed closer to the first impeller I1 than the second impeller I2. The motor M is disposed closer to the first blower B1. The first heat exchanger H1 is not configured to protrude toward the rotation axis S between the first blower B1 and the second blower B2. The second heat exchanger H2 is configured to protrude toward the rotation axis S between the first blower B1 and the second blower B2. Only the second heat exchanger H2 around the second blower B2 on the side farther from the motor M has a protruding portion that protrudes toward the rotation axis S.

According to the heat exchange device 100 according to the third embodiment, the motor M is disposed between the first impeller I1 and the second impeller I2 in the first direction D1, and is disposed closer to the first impeller I1 than the second impeller I2. The first heat exchange section H1 is not configured to protrude toward the rotation axis S between the first blower section B1 and the second blower section B2, and the second heat exchange section H2 is configured to protrude toward the rotation axis S between the first blower section B1 and the second blower section B2. This allows the space between the motor M and the first impeller I1 to be reduced. In addition, since the protruding portion of the first heat exchange section H1 is not manufactured, the number of bends required to manufacture the protruding portion of the heat exchanger HE can be reduced. Furthermore, by extending the protruding portion of the second heat exchange section H2 toward the first heat exchange section H1, the effect of increasing the heat transfer area of the heat exchanger HE can be obtained.

Next, with reference to Figures 12 and 13, we will explain variants 1 and 2 of the heat exchanger 100 according to embodiment 3.

Referring to FIG. 12, in the first modification of the heat exchange device 100 according to the third embodiment, a portion of the motor M is inserted inside the first housing C1 of the first blower B1.

In the first variant of the heat exchanger 100 according to the third embodiment, the space between the motor M and the first impeller I1 can be further reduced.

Referring to FIG. 13, in the second modification of the heat exchange device 100 according to the third embodiment, the first heat exchange section H1 is larger than the second heat exchange section H2. The diameter of the first impeller I1 of the first heat exchange section H1 is larger than the diameter of the second impeller I2 of the second heat exchange section H2. In other words, the diameter of the first impeller I1 of the first heat exchange section H1, which is disposed closer to the motor M, is larger than the diameter of the second impeller I2 of the second heat exchange section H2, which is disposed farther from the motor M.

In the second modification of the heat exchange device 100 according to the third embodiment, the diameter of the first impeller I1 of the first heat exchange section H1 is larger than the diameter of the second impeller I2 of the second heat exchange section H2. Therefore, by compensating for the reduction in air volume caused by the resistance of the motor M, it is possible to suppress the reduction in the heat transfer performance of the heat exchanger HE.

Embodiment 4.
Unless otherwise specified, the heat exchanger 100 according to the fourth embodiment has the same configuration, operation, and effects as the heat exchanger 100 according to the second embodiment.

Referring to FIG. 14, the heat exchange device 100 according to the fourth embodiment further includes a partition member PM. The partition member PM is connected to the motor M. The partition member PM is arranged to separate the first heat exchange section H1 and the second heat exchange section H2. The partition member PM may be configured in a plate shape. The partition member PM is arranged between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1, and protrudes outward from the first heat exchange section H1 and the second heat exchange section H2 in the second direction D2. The outer end of the partition member PM is arranged outward from the outer ends of the first heat exchange section H1 and the second heat exchange section H2 in the second direction D2. In the second direction D2, the distance L3 from the rotation axis S to the outer end of the partition member PM is longer than the distance L4 from the rotation axis S to the outer ends of the first heat exchange section H1 and the second heat exchange section H2. The partition member PM may be a motor support for fixing the motor M.

According to the heat exchange device 100 of the fourth embodiment, the partition member PM is disposed between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1, and protrudes outward beyond the first heat exchange section H1 and the second heat exchange section H2 in the second direction D2. Therefore, the partition member PM functions as a partition plate for the airflow, and can regulate the airflow. In addition, the partition member PM can prevent air that has passed through either the first heat exchange section H1 or the second heat exchange section H2 from flowing into the other of the first heat exchange section H1 and the second heat exchange section H2. This can improve the heat transfer performance of the heat exchanger HE.

Embodiment 5.
Unless otherwise specified, the heat exchanger 100 according to the fifth embodiment has the same configuration, operation, and effects as the heat exchanger 100 according to the second embodiment.

Referring to FIG. 15, the heat exchange device 100 according to the fifth embodiment further includes a cover member CM. The cover member CM surrounds the motor M. The cover member CM is configured to surround at least a portion of the motor M. The cover member CM is disposed between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1. The cover member CM may be a motor support for fixing the motor M.

According to the heat exchange device 100 of embodiment 5, the cover member CM surrounds the motor M and is disposed between the first heat exchange section H1 and the second heat exchange section H2 in the first direction D1. Therefore, the cover member CM can prevent the air that has passed through the first heat exchange section H1 and the second heat exchange section H2 from coming into direct contact with the motor M. Therefore, it is possible to prevent a decrease in efficiency due to a rise in the temperature of the motor M.

The above-described embodiments can be combined as appropriate.
The embodiments disclosed herein should be considered to be illustrative and not restrictive in all respects. The scope of the present disclosure is defined by the claims, not the above description, and is intended to include all modifications within the meaning and scope of the claims.

1 compressor, 2 four-way valve, 3 outdoor heat exchanger, 4 expansion valve, 5 indoor heat exchanger, 6 outdoor blower, 7 indoor blower, 100 heat exchange device, 101 outdoor unit, 102 indoor unit, 1000 air conditioner, AI intake, AO outlet, B1 first blower section, B2 second blower section, BL blade, C1 first housing, C2 second housing, CB centrifugal blower, D1 first direction, D2 second direction, H1 first heat exchange section, H2 second heat exchange section, HE heat exchanger, I1 first impeller, I2 second impeller, M motor, MP main plate, S rotating shaft, SP space.

Claims (11)

A heat exchanger;
a centrifugal blower configured to blow air to the heat exchanger,
The centrifugal blower includes a first blowing section having a first impeller, a second blowing section having a second impeller facing the first impeller, and a rotating shaft extending in a first direction in which the first impeller and the second impeller face each other and connected to the first impeller and the second impeller,
The heat exchanger has a first heat exchange section and a second heat exchange section,
the first heat exchange unit is disposed on one side of the first blower unit in a second direction perpendicular to the first direction and on an opposite side of the second blower unit with respect to the first blower unit in the first direction,
The second heat exchange unit is disposed on the opposite side of the second blower unit from the first blower unit in the first direction and across from the second blower unit in the second direction. The heat exchange device according to claim 1, wherein the first impeller and the second impeller are configured to be rotatable by the rotation of the rotating shaft. The heat exchange device according to claim 2, wherein at least one of the first heat exchange section and the second heat exchange section is configured to extend toward the rotation axis between the first blower section and the second blower section. The first blower unit has a first housing that houses the first impeller,
The second blower unit has a second housing that houses the second impeller,
Each of the first impeller and the second impeller has a main plate connected to the rotating shaft and a plurality of blades arranged on the main plate in a circumferential direction of the rotating shaft,
Each of the first housing and the second housing has an intake port communicating with a space in which the main plate and the plurality of blades are arranged, and an exhaust port communicating with the space,
4. The heat exchange device according to claim 3, wherein the centrifugal blower is configured such that, as the first impeller and the second impeller rotate, air sucked in through the intake port in each of the first housing and the second housing passes through the space and is discharged from the exhaust port. The centrifugal blower has a motor configured to rotate the rotary shaft,
The heat exchange device according to claim 3 , wherein at least a portion of the motor is disposed on an opposite side of the second heat exchange portion to the first heat exchange portion in the first direction. The centrifugal blower has a motor configured to rotate the rotary shaft,
The heat exchange device according to claim 3 or 4, wherein the motor is disposed between the first heat exchange unit and the second heat exchange unit in the first direction and disposed with a gap between the first heat exchange unit and the second heat exchange unit. The centrifugal blower has a motor configured to rotate the rotary shaft,
The heat exchanger device according to claim 3 or 4, wherein the motor is arranged between the first blowing section and the second blowing section in the first direction, and arranged so as to overlap with at least one of the first heat exchange section and the second heat exchange section in the second direction. The centrifugal blower has a motor configured to rotate the rotary shaft,
the motor is disposed between the first impeller and the second impeller in the first direction and is disposed closer to the first impeller than the second impeller;
The first heat exchange unit is not configured to protrude toward the rotation shaft between the first blower unit and the second blower unit,
The heat exchange device according to claim 3 , wherein the second heat exchange section is configured to protrude toward the rotation shaft between the first blower section and the second blower section. The heat exchange device according to claim 8, wherein the diameter of the first impeller of the first heat exchange section is greater than the diameter of the second impeller of the second heat exchange section. A partition member connected to the motor is further provided.
A heat exchanger device as described in any one of claims 6 to 9, wherein a front partition member is arranged between the first heat exchange section and the second heat exchange section in the first direction, and protrudes outward further than the first heat exchange section and the second heat exchange section in the second direction. A cover member that surrounds the motor is further provided.
The heat exchange device according to any one of claims 6 to 9, wherein the cover member is disposed between the first heat exchange portion and the second heat exchange portion in the first direction.

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